EP1538336A1 - Dosierpumpe - Google Patents
Dosierpumpe Download PDFInfo
- Publication number
- EP1538336A1 EP1538336A1 EP03027090A EP03027090A EP1538336A1 EP 1538336 A1 EP1538336 A1 EP 1538336A1 EP 03027090 A EP03027090 A EP 03027090A EP 03027090 A EP03027090 A EP 03027090A EP 1538336 A1 EP1538336 A1 EP 1538336A1
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- EP
- European Patent Office
- Prior art keywords
- piston
- bore
- stop
- pump according
- dosing pump
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/007—Cylinder heads
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/16—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by adjusting the capacity of dead spaces of working chambers
Definitions
- the invention relates to a metering pump for a pumped, with a Pump housing and a cylinder bore formed in the pump housing, in the one suction hole and a discharge hole for the feeder or the Squeezing out the pumped material and in the two pistons, in the cylinder bore, sweeping the area of the suction hole and the discharge hole, with seal against the cylinder wall slippery and without rigid Mutual coupling are arranged and with their front sides to the Adjacent to each other to be moved, with one on the first piston attacking alternating drive in its axial direction with a movement phase approaching the second piston, a first stop to itself the second piston at it at approach of the first piston in particular against a biasing force retrograde movement moved and if necessary, but not in any case, achieved or which he also touched permanently, and one from the second piston in his Movement towards the first piston reached adjustable second Attack.
- Metering pumps are versatile, for example in chemistry and Pharmacy, for the vaccination of fluid streams or for the delivery of Lubricant on friction surfaces.
- To the latter application is an example called the lubrication of transport rails, where weight-bearing Sliding slide, for example, moved along by a traction drive.
- weight-bearing Sliding slide for example, moved along by a traction drive.
- slaughterhouses where in irregular Distances loads such as half pigs hooked on are suspended, transported along the rail, where the hooks hang.
- central lubrication machines are known which from time to time to predetermined points, each with a pipeline connected to the lube, small amounts of the lubricant apply the rail.
- Double-piston pumps are particularly well suited as metering pumps for small quantities. which are known in various designs.
- a metering pump in the form of a double piston pump is for example known from US 3 302 578 A.
- the cylinder bore slide axially one behind the other two pistons, one of which is driven by a drive unit and the other of the first piston via an external friction rail with is driven, this second piston moves between two stops one of which is adjustable and from the moment the attack is reached held stationary by sliding friction on the friction rail.
- the well-known Pump proves to be inaccurate in terms of the pump function exploited friction forces and as expensive in terms of guides due to the occurring bending forces.
- From DE 25 00 473 A is also a metering pump, especially as Feed pump for a diaphragm pump, also known as two in one Cylinder bore located piston, one of which is a reciprocating Working piston and the other an adjustable, during the pumping process stationary adjusting piston are.
- the adjusting piston is with a wedge connected to the inclined surface with a with an adjusting screw connected further wedge attacks, whereby the adjusting piston so adjusted can be that its face more or less deep in the cylinder bore lies.
- the movement reversal of the longitudinal adjustment caused by the wedge arrangement in a transverse adjustment results in a cumbersome, trouble-prone Construction.
- EP 1 270 938 A is a metering pump with a cylinder bore known in the axially offset a suction hole and a discharge hole open and in the two pin-shaped pistons work against each other, both are forcibly moved.
- the pump should in particular small amounts of adhesive be delivered. For a change in the flow rate is at this level nothing planned for the technology.
- EP 1 195 518 A is a metering pump with two with a common Axis aligned pistons, namely a fixed and a through a Piezoaktor reciprocating longitudinally movable piston and with one in the same Direction of moving housing described.
- a dosage to be dosed Volume can be the maximum distance between the piston end faces be changed that sits in a holder an adjusting screw, the acts on the piezoelectric actuator and selected by adjusting the piston position can be.
- the pistons are forced relative to each other.
- the attack of the Adjusting screw on the drive, namely on the piezoelectric actuator leads to other drive types, For example, in a cam drive, too expensive and thus heavy and fault-prone designs.
- the invention is an easy to produce with a few components, Robust and insensitive construction for metering the flow rate the pump are created. This is based on a metering pump of At the beginning specified genus thereby enables the second stop at a relative to the pump housing along the axis of the cylinder bore sitting by means of threaded adjustable by twisting screw. With the second stop the delivery stroke is set.
- the screw thus forms a kind of small extension of the pump housing, the movable and adjustable components of the pump can be coaxial and thus free from bending stress be arranged and the volume adjustment is done by simply twisting the screw, in turn, by latching or locking mechanisms against an unwanted twisting can be ensured.
- the metering pump are preferably two basic types and also Combinations thereof possible, namely on the one hand such that in the Suction bore and the delivery bore are a suction or a pressure valve, and on the other hand such that the suction hole and the discharge hole offset along the cylinder axis into the cylinder bore and open the displaceable over the mouth points away piston on passage or blocking are controllable.
- the pistons are partially expediently under a preload force, the piston movement in one the possible directions generated, for which in particular springs, preferably Coil springs, come into question.
- Coil springs can be due to their cylindrical basic configuration best in the pump design integrate.
- a first preferred spring construction is that the second piston is urged by spring force in the direction of the first piston and in this direction at the second sleeve connected to the screw Stop finds an end to its trajectory; and a second basic construction is that the second piston by spring force against the Direction is pressed to the first piston and in this pressing direction on a slidable stop parallel to the axial direction of the cylinder bore End of his trajectory finds, with this sliding stop in turn, between two spaced apart along the cylinder axis Strokes is displaced, namely on the one hand by spring force in the direction is pressed to the first piston and in this direction on with the screw connected second stop finds an end to its trajectory and on the other hand, on a housing-fixed stop one end of its trajectory place.
- the Pump housing, the piston and the screw sleeve have for all these design variants a consistent basic construction.
- the screw are two preferred Constructions available according to a particularly preferred embodiment be applied together.
- the first construction exists in that the threaded sleeve rotatably screwed onto a bolt is, which is fixed to the pump housing, wherein the pump housing, a bracket is attached, extending to the area of the extension of the cylinder axis extends and in this area has a threaded bore into which the adjustable bolt is screwed in and in his position is fixed.
- the screw if necessary in addition to the screw connection with the bolt, with an external thread into a threaded bore, which is coaxial with the cylinder bore, in the pump housing, the larger compared to the cylinder bore diameter has screwed, twisted.
- the adjustable metering pump according to the invention is of simple, robust Construction. It can be used in various construction variants using essentially the same components are produced. Besides, they are Multiple pumps possible in a common pump housing a Contain a plurality of cylinder bores whose delivery rates by a common adjustment installation can be adjusted.
- the drawings show sections in varying magnifications by metering pumps according to the invention in various embodiments.
- the metering pumps are essentially of cylindrical basic shape.
- FIGS. 1 to 4 show a metering pump according to a first basic embodiment in longitudinal section in different work phases. The basic construction will be explained with reference to FIG. 1, in which the working phase in the Waiting position or at the beginning of the pumping stroke is shown.
- the metering pump has a pump housing 11 in which centrally and coaxial with the pump housing 11, a cylinder bore 12 is located.
- a cylinder bore 12 is located in both sides in the housing 11th Blind holes 13 and 14 of compared to the cylinder bore 12 enlarged Diameter formed, each with one in a radial plane lying diameter stage 15 or 16.
- two are each at the end over the diameter stage 15 or 16 projecting pin-shaped piston, namely a first piston 17 and a second piston 18 are arranged in known manner with sealing against the cylinder wall in the cylinder bore 12 slide. They have oppositely directed end faces 19 and 20, respectively which are in the working position of Fig. 2 at a distance from each other and between include a pumping space 21.
- the axis of the cylinder bore 12 and in the illustrated embodiment of the entire pump housing 11 is with 22 denotes.
- the first piston 17 continues outward in an external plunger 25, on which an unillustrated drive engages, the plunger 25 in alternating or according to the control in each case individual longitudinal movements in the direction the axis 22 offset. It may, for example, be an electrical, pneumatic or a cam or crank drive act.
- the blind bore 13 is located near the open end in an annular groove of the Pump housing 11 a radially outwardly resilient washer 26, through which Ring opening of the piston 17 is inserted, and in an annular groove in the piston 17 is a radially inwardly resilient annular disc 27, on the one hand an annular stop on the annular disc 26 finds and on the other hand a Support for a helical compression spring 28, which is in the blind bore 13 coaxial with this and the piston 17, the latter surrounding, is arranged and on the other hand supported on the diameter stage 15.
- the first piston 17 is thus opposed by the drive, which acts axially on the plunger 25 the force of the spring 28 is advanced in the cylinder bore 12 and after the end the driving force by the spring 28 retracted again.
- the on the side of the second piston 18 coaxially in the pump housing 11th located blind bore 14 is made in two stages, with a to the cylinder bore 12 subsequent part 29 of smaller diameter and one at the Front side of the pump housing 11 opening portion 30 of larger diameter.
- a thread 31 is cut, and in this is a screw 32 screwed.
- This in turn has an axial bore, which consists of a directed to the cylinder bore 12 first bore 37 and one of the Cylinder bore 12 facing away from second bore 38, wherein the Bore 38 has a smaller diameter and with an internal thread 39 is provided.
- a diameter stage 40th Between the first and the second bore 37, 38 of the threaded sleeve 32 is a diameter stage 40th
- a radial outwardly resilient washer 44 is used, which serves as a stop in the direction of Cylinder bore 12 for sliding in the first bore 37, with the Piston 18 rigidly connected stop plate 45 is used.
- a helical compression spring 46th clamped, the stop disc 45 and the second piston 18 in the direction to the first piston 17 presses.
- a threaded bolt 49 is screwed, the End face 50 serves as a stop for the stop plate 45.
- the threaded bolt 49 is adjustable and then locked by a lock nut 51. He sits for this in a bracket 52 which is fixedly secured to the pump housing 11 and the shape a twice bent strip, a cage or even a cap can. In the case of the cap, however, it must have an opening in one place, by which the screw sleeve 32 can be reached for their adjustment.
- the threaded bolt 49 is screwed into the bracket 52 in the illustrated embodiment and the lock nut 51 is the non-positive locking of Position of the threaded bolt 49.
- the thread pitches of the thread 31 on the one hand and the thread 39 on the other hand are the same in the sense that the Screw sleeve 32 rotatable and thereby, due to the two threads each by an equal amount, forward and backward is. This shifts the stopper plate 45, which by the spring 46 to the annular disc 44th is pressed, together with the latter in the bore part 29 relative to the pump housing 11 back and forth.
- a snap mechanism 54 consisting of a helical compression spring 55, one of these radially advanced ball 56 and circumferential grooves 57, the run along generatrices of the screw sleeve 32, prevents an independent unintentional rotation of the screw sleeve 32 (FIG. 5).
- Fig. 6 a On the screw 32nd engaging spindle mechanism 58.
- the threaded bolt 49 is in Bracket 52 has been adjusted and fixed at a first setting and will be around does not change during normal operation of the metering pump.
- the location of the mouths of these holes in the cylinder bore 12 is in the of the end faces 19 and 20 of the piston 17 and 18 at their pumping movements swept cylinder bore area.
- the suction hole 61 is connected to a pumping gas tank, not shown, z. B. one Lubricant tank, connected.
- Figs 1 and 2 the pump is shown with a setting in which the pumping chamber 21 large and accordingly expressed per piston stroke Pumpgutvolumen also is large. This has been adjusted by the Screw sleeve 32 in the part 29 of the blind bore 14 further unscrewed to the rear is and thus the second piston 18 in its return movement to the squeezing of the pumped material after a short movement due to the Impact of the stop plate 45 comes to a stop on the annular disc 44.
- Fig. 4 shows the initial position for minimum pumping volume, with complete screwed screw 32.
- the end face 50 of the threaded bolt 49 is in the same place as in Fig.n 1 to 3.
- the second piston 18 then follows the first piston 17 in the return movement to very close at its end position, and between the end faces 19 and 20 then still resulting very small distance determines the minimum pumping volume.
- Fig. 7 shows an embodiment with a relatively shorter first piston 17, whereby the pumping space 21 in the initial position accordingly is larger.
- the spring 46 also omitted.
- the second piston 18 is then at the Backward movement of the first piston 17 by the otherwise arising Vacuum tightened.
- the spring 28 can be omitted. The pushing back of the first piston 17 then worried the pressure of the pumped material.
- FIGs. 8 and 9 show a construction in which the spring 46 is omitted is and the threaded bolt 49 not in the bracket 52, but in the screw 32 is fixed. He is screwed in this far enough that the stop disc 45 fixed between the annular disc 44 and the end face 50 of the threaded bolt is clamped.
- the second piston 18 is in this case rigid with the threaded sleeve 32nd connected and by their rotation forward or backward, he moves but not during the pumping.
- FIG. 8 shows the initial position and FIG. 9 the end position of the pumping club.
- the pump according to Fig.n 1 to 7 can also be installed in the setting be that the threaded bolt 49 is withdrawn so far that him the stop disc 45 is no longer reached (Fig. 10), since previously the spring 46th leads to a stop of the second piston 18.
- the bolt 49 also completely omitted, which is shown in Fig. 11.
- the first stop is in In this case, an elastically resilient, yielding stop.
- This variant has the optionally desired consequence that only at a pressure drop in the Support line additional pumped material is promoted, so more or less on Constant pressure is pumped, and is also advantageous if the on the Tappet 25 acting drive width is not uniform and possibly over the degree goes beyond that by the stop of the second piston 18 at the End face 50 is given. Then the pump could possibly be damaged become. This is due to the elastic stop, as it is the force of the spring 46 represents avoided.
- the basic embodiment according to FIGS. 12 to 25 differs 1 to 11 on the one hand by the fact that the suction hole 61st and the discharge hole 63 offset into the cylinder bore 12 open, and on the other hand characterized in that the second piston 18 in the direction of the stop disc 45 is spring loaded and in the opposite direction in its Movement is limited by a stop.
- FIGS. 19 to 21 show the working position with the middle position of the screw sleeve 32 and thus in a setting for medium pumping volume
- FIG. 22 to 24 at maximum screwed screw 32 and thus in one setting for minimal pump volume.
- the suction hole is located 61 axially offset closer to the region of the first piston 17 and is not here with the check valve 62 equipped.
- the discharge hole 63 is located axially is offset closer to the area of the second piston 18 and is here with the Check valve 64 provided. The distance between the mouths of the two holes corresponds to the maximum length of the pump room 21.
- On the second Piston 18 is located in the vicinity of which the pump chamber 21 facing away End one in a circumferential groove radially inwardly resiliently inserted Ring disc 71, between the and the diameter stage 16 a helical compression spring 72 is used.
- a stop sleeve 73 To a partial length of the spring 72 runs, of the Starting diameter stage 16, a stop sleeve 73, the way the second piston 18 into the pumping space 21 into limited.
- the outer diameter the stop sleeve 73 is smaller than the inner diameter of the part 29th the screw sleeve 32 so that the stop sleeve 73 screwing the Screw sleeve 32 not hindered. Otherwise, the construction of the according to Fig.n 1 to 7.
- Fig. 13 shows the beginning of the advance of the first piston 17 and Fig. 14 a a little later phase in which the pumped material is squeezed out.
- the pushes in Fig. 13 as an arrow indicated drive the first piston 17 initially at the mouth of the Suction bore 61 over, with the extent displaced pumped into this Bore is pushed back.
- the end face 19 of the first piston 17 passes this mouth, so the suction hole is blocked and the pumped in the pump chamber 21 pushes the second piston 18, from the beginning of the Stop disc 45 abuts, against the force of the spring 46 with this rear.
- the second piston 18 has the mouth the discharge hole 63 is released, so that the check valve 64 is opened is and the pumped material is discharged.
- the end face 19 of the first piston 17th comes up to the end face 20 of the second piston 18, the in turn, reaches the stop 50 in this work phase expediently (Fig. 15). If he does not reach him, then in the case of a continued drive movement also the second piston 18 against the force of the spring 46 yet further pushed out in the drawing to the right from the cylinder bore.
- the delivered in the workflow according to the Fig.n 12 to 15 per stroke Amount of pumped material is due to the distance between the mouths of the Drill holes 61 and 63 determined. This is the maximum possible pumping amount. In the illustrated embodiment corresponds to the maximum range of motion the drive and thus the piston 17 the distance between the mouths the holes 61 and 63 in the cylinder bore 12. In this setting for maximum pumping volume is at the beginning of the stroke of the piston 18 on the Disc 45 on stop 50 at.
- the dose amount can be reduced, as in the example of Figs. 19 to 21 are shown.
- the screw 32 is deeper into the pump housing 11 screwed in, causing the serving as a stop washer 45 is moved closer to the pump chamber 21.
- 19 shows the resting and waiting phase, in the front side 19 of the first piston 17, the mouth of the suction hole 61 touched.
- the first piston pushes first 17 a small amount of the volume of the pumped material in the suction hole 61st back and reaches the position of Fig. 20, in which he begins, over the Pump volume to push back the second piston 18 against the action of the spring 46.
- This pushing back takes place until the pumping space 21 the mouth reaches the discharge hole 64 and the piston 18 via the disc 45 the Stop 50 is reached, so that the piston 17 is then under pressure of the Pumping material to the end face 20 of the piston 18 approximates.
- Figs. 22 to 24 show the same working phases for a minimum Volume.
- the end faces 19 and 20 are little more than the Diameter of the mouth of the suction hole 61 spaced.
- the pumping chamber 21 is largely emptied back into the suction bore 61 becomes.
- the reduced to almost zero pumping space 21 moves in the Area of the mouth of the discharge hole 63, due to the counterforce the spring 46 and the stopper 50 located in the pump chamber 21 Residual volume is delivered.
- the construction can be simplified when the pumped material is under pressure.
- the spring 72 are omitted.
- the provision of the first piston 17 by the force of spring 28 In general, it is also possible on the piston 17 to attack a crank, on the other hand to a with a shaft connected crank pin is seated, so that the piston 17 in both Directions is forced by the shaft.
- Fig. 25 shows such a design, at the end of the pumping stroke.
- the second Piston 18 by continued drive thrust, where appropriate after a rotation the screw sleeve 32 in the rest position still further to the rear Nevertheless, the pump volume would not be higher, because after the Sweeping the mouth of the dispensing bore 63 through the first piston 17 the further pump delivery is blocked.
- the pump housing 11 may also have more than one cylinder bore where possible, for each cylinder and piston pair to use its own screw 49, or more or all cylinders and Adjust piston pairs with a common threaded sleeve.
- a need for such a multi-cylinder pump z. B. arise in a chain lubrication, in which the chain progresses intermittently and in their short Rest periods is lubricated at the hinge points.
- four Cylinders in the pump housing can have four hinge points of the chain at the same time be lubricated.
- Another application could be more specific in the preparation Mixtures are. Unless the pump is to the intended use is specially set up, even with synchronous adjustment by only a single screw different amounts of components of a Mixture predetermined by different diameters of the cylinder bores become.
- FIGS. 26 to 29 show an embodiment with two cylinder bores and FIGS. 30 to 33 show an embodiment with four cylinder bores.
- the embodiment according to the Fig.n 30 to 33 contains four in cross-section in Square arranged cylinder bores 12a, 12b, 12c and 12d in cross section octagonal pump housing 11.
- the octagons are used to facilitate Arrangement of four separate discharge bores 63a, 63b, 63c and 63d, in a common radial plane star-shaped of the four cylinder bores out.
- suction holes 61a, 61b, 61c and 61d are shown in the illustrated Example separate for individual cylinder bores available to a faster suction and thereby achieve a higher pumping rate, they but could, what does not matter, from cylinder bore to Cylinder bore be placed in a series arrangement.
- Fig. 31 shows, go in the example shown, the suction holes 61a and 61b of a common connection volume 81 and the suction holes 61c and 61d of a common connection volume 82.
- first pistons 17a, 17b, 17c and 17d Of four first pistons 17a, 17b, 17c and 17d, only the pistons are shown in FIG 17a and 17b, and second pistons 18a, 18b, 18c and 18d are shown in FIG. 33 recognizable. They are connected together with the stop plate 45 or are also loose and pressed only by the action of force on this.
- Ring disk 31 of FIG. 12 corresponds to FIGS. 30 and 33 an annular disk 71 a, which is attached to the four pistons 18 a to 18 d and by a Diameter stage of these pistons under the force of the spring 72 to this diameter stage is pressed.
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Abstract
Description
- Fig.n 1 bis 4
- Längsschnitte durch eine erste Grund-Ausführungsform der Dosierpumpe in verschiedenen Arbeitsstellungen;
- Fig. 5
- einen Querschnitt durch die dargestellte Ausführungsform in einer Ebene (5)-(5) in Fig. 1;
- Fig. 6
- eine gegenüber der Ausführung von Fig. 5 abgewandelte Ausführung;
- Fig.n 7 bis 11
- Abwandlungen der Ausführungsform nach den Fig.n 1 bis 4 in entsprechenden Längsschnittdarstellungen;
- Fig.n 12 bis 18
- Längsschnitte durch eine Dosierpumpe gemäß einer zweiten GrundAusführungsform in verschiedenen Arbeitsstellungen bei Einstellung für ein maximales Fördervolumen;
- Fig.n 19 bis 21
- Darstellungen entsprechend den Fig.n 12 bis 14 bei einer Einstellung für ein mittleres Fördervolumen;
- Fig.n 22 bis 24
- Darstellungen entsprechend den Fig.n 12, 13 und 15 bei einer Einstellung für ein minimales Fördervolumen;
- Fig. 25
- einen Längsschnitt durch eine Dosierpumpe gemäß einer Abwandlung der zweiten Grund-Ausführungsform;
- Fig. 26
- einen Längsschnitt durch eine weitere Abwandlung der zweiten Grund-Ausführungsform, nämlich mit zwei parallelen Zylinderbohrungen;
- Fig.n 27 bis 29
- Querschnitte durch die Dosierpumpe von Fig. 26 in Schnittebenen (27)-(27), (28)-(28), bzw. (29)-(29);
- Fig. 30
- einen Längsschnitt durch eine weitere Abwandlung der zweiten Grund-Ausführungsform, nämlich mit vier parallelen Zylinderbohrungen;
- Fig.n 31 bis 33
- Querschnitte durch die Dosierpumpe von Fig. 30 in Schnittebenen (31)-(31), (32)-(32) bzw. (33)-(33).
Claims (14)
- Dosierpumpe für ein Pumpgut, mit einem Pumpengehäuse (11) und einer im Pumpengehäuse entlang einer Längsache (22) gebildeten Zylinderbohrung (12), in die eine Ansaugbohrung (61) und eine Abgabebohrung (63) für den Einzug bzw. das Auspressen des Pumpguts münden und in der zwei Kolben (17, 18), die in der Zylinderbohrung (12), den Bereich der Ansaugbohrung (61) und der Abgabebohrung (63) überstreichend, mit Abdichtung gegen die Zylinderwand gleitfähig und ohne starre gegenseitige Kopplung angeordnet sind und mit ihren Stirnseiten (19, 20) bis zur Aneinanderlage aufeinander zu bewegbar sind, mit einem am ersten Kolben (17) angreifenden alternierenden Antrieb (77, 78, 25) in seiner Axialrichtung mit einer Bewegungsphase der Annäherung an den zweiten Kolben (18), einem ersten Anschlag (50, 46), auf den zu sich der zweite Kolben (18) bei seiner bei der Annäherung des ersten Kolbens (17) erfolgenden Rückwärtsbewegung bewegt, und einem vom zweiten Kolben (18) in seiner Bewegung in Richtung zum ersten Kolben (17) erreichten verstellbaren zweiten Anschlag (44), dadurch gekennzeichnet, daß der zweite Anschlag (44) an einer relativ zum Pumpengehäuse (11) entlang der Achse (22) der Zylinderbohrung (12) mittels Gewinde (31, 39) durch Verdrehung verstellbaren Schraubhülse (32) sitzt.
- Dosierpumpe nach Anspruch 1, dadurch gekennzeichnet, daß sich in der Ansaugbohrung (61) und/oder der Abgabebohrung (63) ein Saug- (62) bzw. ein Druckventil (64) befinden.
- Dosierpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Ansaugbohrung (61) und die Abgabebohrung (63) entlang der Zylinderachse (22) versetzt in die Zylinderbohrung (12) münden und durch die sich über die Mündungsstelle hinweg verschiebbaren Kolben (17, 18) auf Durchlaß oder Sperrung steuerbar sind.
- Dosierpumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der zweite Kolben (18) durch Federkraft (46) in die Richtung zum ersten Kolben (17) gedrückt ist und in dieser Richtung an dem mit der Schraubhülse (32) verbundenen zweiten Anschlag (44) ein Ende seiner Bewegungsbahn findet.
- Dosierpumpe nach Anspruch 4, dadurch gekennzeichnet, daß der zweite Kolben (18) mit einer radialen Scheibe (45) gekoppelt ist, die sich an den zweiten Anschlag (44) anlegt.
- Dosierpumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der zweite Kolben (18) durch Federkraft (72) entgegen der Richtung zum ersten Kolben (17) gedrückt ist und in dieser Drückrichtung an einem parallel zur Achse (22) der Zylinderbohrung (12) verschiebbaren Anschlag (45) ein Ende seiner Bewegungsbahn findet, wobei dieser verschiebbare Anschlag (45) seinerseits zwischen den beiden im Abstand entlang der Zylinderachse angeordneten Anschlägen (44, 50) verschiebbar ist, nämlich einerseits durch Federkraft (46) in die Richtung zum ersten Kolben (17) gedrückt ist und in dieser Richtung am mit der Schraubhülse (32) verbundenen zweiten Anschlag (44) ein Ende seiner Bewegungsbahn findet und andererseits am gehäusefesten ersten Anschlag (49, 50) ein Ende seiner Bewegungsbahn findet.
- Dosierpumpe nach Anspruch 6, dadurch gekennzeichnet, daß der verschiebbare Anschlag die Form einer radialen Scheibe (45) hat.
- Dosierpumpe nach Anspruch 5 oder 7, dadurch gekennzeichnet, daß der Abstand zwischen dem ersten Anschlag (50) und dem zweiten Anschlag (44) größer/gleich der Dicke der Scheibe (45) ist.
- Dosierpumpe nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, daß die Schraubhülse (32) verdrehbar auf einen Gewindebolzen (49) aufgeschraubt ist, der am Pumpengehäuse (11) fixiert ist.
- Dosierpumpe nach Anspruch 9, dadurch gekennzeichnet, daß am Pumpengehäuse (11) ein Bügel (52) befestigt ist, der sich bis in den Bereich der Verlängerung der Zylinderachse (22) erstreckt und in diesem Bereich eine Gewindebohrung aufweist, in die der zunächst verstellbare Gewindebolzen (49) eingeschraubt ist und in der er in seiner Stellung fixiert ist.
- Dosierpumpe nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß die Schraubhülse (32), gegebenenfalls zusätzlich zur Schraubverbindung mit dem Gewindebolzen (49), mit einem Außengewinde (31) in eine zur Zylinderbohrung (12) koaxiale Gewindebohrung im Pumpengehäuse (11), die im Vergleich zur Zylinderbohrung (12) einen größeren Durchmesser hat, verdrehbar eingeschraubt ist.
- Dosierpumpe nach einem der Ansprüche 9 bis 11, dadurch gekennzeichnet, daß die Schraubhülse (32) in ihrer Drehstellung durch einen Schnappmechanismus (54) lösbar fixiert ist.
- Dosierpumpe nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, daß im Pumpengehäuse eine Mehrzahl paralleler Zylinderbohrungen (12a, 12b, 12c, 12d) gebildet ist, die jeweils die beiden Kolben enthalten und an eine Ansaugbohrung (61a ... 61d) und eine Abgabebohrung (63a ... 63d) angeschlossen sind, und daß der erste Anschlag (50, 46) und der an der Schraubhülse (32) sitzende zweite Anschlag (44) für die zweiten Kolben (18a ... 18d) gemeinsam dienen.
- Dosierpumpe nach einem der Ansprüche 1 bis 13, gekennzeichnet durch die Verwendung zur Schmierung einer Gleittransportbahn (2) für den Transport diskreter Transporteinheiten (3, 4).
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT03027090T ATE375451T1 (de) | 2003-11-25 | 2003-11-25 | Dosierpumpe |
EP03027090A EP1538336B1 (de) | 2003-11-25 | 2003-11-25 | Dosierpumpe |
DE50308362T DE50308362D1 (de) | 2003-11-25 | 2003-11-25 | Dosierpumpe |
ES03027090T ES2298464T3 (es) | 2003-11-25 | 2003-11-25 | Bomba dosificadora. |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP03027090A EP1538336B1 (de) | 2003-11-25 | 2003-11-25 | Dosierpumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1538336A1 true EP1538336A1 (de) | 2005-06-08 |
EP1538336B1 EP1538336B1 (de) | 2007-10-10 |
Family
ID=34442872
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03027090A Expired - Lifetime EP1538336B1 (de) | 2003-11-25 | 2003-11-25 | Dosierpumpe |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1538336B1 (de) |
AT (1) | ATE375451T1 (de) |
DE (1) | DE50308362D1 (de) |
ES (1) | ES2298464T3 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105221400A (zh) * | 2015-10-22 | 2016-01-06 | 宁波合力机泵有限公司 | 一种往复泵无回流变量装置 |
CN108518328A (zh) * | 2018-06-15 | 2018-09-11 | 焦作市恒利水文地质工程有限责任公司 | 一种泥浆泵高压泵头 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3302578A (en) * | 1965-04-28 | 1967-02-07 | H V Hardman Co Inc | Metering pump |
DE2500473A1 (de) * | 1975-01-08 | 1976-07-15 | Franz Orlita | Dosierpumpe, insbesondere fuer kleine foerdermengen |
US4405294A (en) * | 1980-10-11 | 1983-09-20 | Dragerwerk Ag | Dosing pump |
-
2003
- 2003-11-25 AT AT03027090T patent/ATE375451T1/de not_active IP Right Cessation
- 2003-11-25 EP EP03027090A patent/EP1538336B1/de not_active Expired - Lifetime
- 2003-11-25 ES ES03027090T patent/ES2298464T3/es not_active Expired - Lifetime
- 2003-11-25 DE DE50308362T patent/DE50308362D1/de not_active Expired - Lifetime
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3302578A (en) * | 1965-04-28 | 1967-02-07 | H V Hardman Co Inc | Metering pump |
DE2500473A1 (de) * | 1975-01-08 | 1976-07-15 | Franz Orlita | Dosierpumpe, insbesondere fuer kleine foerdermengen |
US4405294A (en) * | 1980-10-11 | 1983-09-20 | Dragerwerk Ag | Dosing pump |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105221400A (zh) * | 2015-10-22 | 2016-01-06 | 宁波合力机泵有限公司 | 一种往复泵无回流变量装置 |
CN108518328A (zh) * | 2018-06-15 | 2018-09-11 | 焦作市恒利水文地质工程有限责任公司 | 一种泥浆泵高压泵头 |
CN108518328B (zh) * | 2018-06-15 | 2024-07-05 | 焦作市恒利水文地质工程有限责任公司 | 一种泥浆泵高压泵头 |
Also Published As
Publication number | Publication date |
---|---|
ATE375451T1 (de) | 2007-10-15 |
EP1538336B1 (de) | 2007-10-10 |
DE50308362D1 (de) | 2007-11-22 |
ES2298464T3 (es) | 2008-05-16 |
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